CN1098478A

CN1098478A - Variable displacement piston type compressor

Info

Publication number: CN1098478A
Application number: CN93118967A
Authority: CN
Inventors: 狩野浩; 寺内清; 深井勇; 小仓俊之
Original assignee: Sanden Corp
Current assignee: Sanden Corp
Priority date: 1992-09-02
Filing date: 1993-09-02
Publication date: 1995-02-08
Anticipated expiration: 2013-09-02
Also published as: KR100226537B1; CA2105346C; AU2855495A; CA2105346A1; JP2572690Y2; AU2855595A; KR940007371A; AU4606293A; AU663615B2; CN1034602C; AU670526B2; US5490767A; AU688070B2; JPH0625573U

Abstract

Piston compressor includes the compressor housing of some cylinders.But the live axle of a wobbler mitered, and be coupled to and somely be subjected to this to drive the piston that in cylinder, moves back and forth in swivel bearing in this housing.Each piston rotation mechanism of setting up defences comprises being disposed in this housing preventing piston first and second anti-rotation device around its rotational to unite.This mechanism can comprise a Device for preventing rotation that form in the heart and comprise two slip surfaces that form at least on piston two radial side in piston.Each slip surface slides on the adjacent sliding surface of adjacent Device for preventing rotation, makes this Device for preventing rotation and adjacent cooperation prevent that piston is around its rotational.

Description

Variable displacement piston type compressor

The present invention relates to a kind of Piston Refrigerant Compreessor, particularly a kind ofly be applicable to oblique tray type compressor automotive air-conditioning system, that have the discharge capacity regulating mechanism.

A kind of oblique tray type compressor automotive air-conditioning system, that have the discharge capacity regulating mechanism that is applicable to is disclosed in 63-93480 Japanese patent application bulletin.As shown in Figure 1, the shell of compressor is the front case of being made by aluminum alloy 1, preceding valve plate 9, and cylinder block 3, back valve plate 4 and rear case 5 constitute.Cylinder block 3 is to be made of front-bank rotor housing 3a that adjoins each other and rear-bank rotor housing 3b.Front case 1 is installed in a side of cylinder block 3 by preceding

valve plate

9,5 opposite sides that are installed in cylinder block 3 by back valve plate 4 of rear case.These casing components constitute one by a grade bolt 6.

In cylinder block 3, constitute one group of cylinder 7 and chamber 8 that is parallel to each other and arranges by front and rear cylinder 3a, 3b.In addition, in cylinder block 3 and rear case 5, be respectively arranged with the clutch shaft bearing 10 and second bearing 11, in order to supports main shaft 12 rotationally.The loop configuration centres of main shaft 12 and cylinder 7.One end 13 of main shaft 12 is passed the main shaft seal bearing 14 that is installed on the front case 1 and is extended to outside the front case 1.The end 13 that is exposed is connected with a magnetic clutch (not shown), thereby makes the driving torque of motor car engine pass to main shaft 12 by magnetic clutch.

A work chamber 15 and a back work chamber 16 also reciprocally inserted in each cylinder 7 before the internal surface of piston 17 and each cylinder 7 defined one jointly.So each piston 17 can reciprocally slide under the effect of the swash plate in being installed in bent axle chamber 8 18.

Swash plate 18 heart position therein has a lug boss, and this lug boss constitutes an arm 19.On position corresponding on the main shaft 12, be provided with plat part 20 with the arm 19 of swash plate 18.Be mounted obliquely within on the main shaft 12 with the swash plate 18 that cooperates of arm 19 by plat part 20.In addition, pin 21 is fixed with the lug boss of swash plate 18.Pin 21 cooperates by the elongated hole 22 on the plat part 20 of a snap ring and main shaft 12.In this structure, swash plate 18 conversion between the less position in bigger position, tilt angle and tilt angle, the pin 21 of swash plate 18 slides in elongated hole 22 simultaneously.The capacity of compressor depends on the tilt angle of swash plate 18.When the tilt angle of swash plate 18 increased, the running length of the piston 17 in the cylinder 7 increased, and the capacity of compressor reduces.The rotating force of main shaft 12 is passed to swash plate 18 by plat part 20 and cooperating of arm 19.Under the driving of main shaft, swash plate 18 moves around its rotational and along its axial direction with main shaft 12.So, swash plate 18 a bottom right loxosis put and a upper right loxosis put between the swing.

The peripheral surface of swash plate 18 is connected with piston 17 by a pair of slide rail 23.Swash plate 18 is inserted into this slidably in the space between the supporting element.Supporting element 23 with swash plate 18 state of contact under form one spherical and be installed in rotation in the groove that adapts to it on the piston 17.Therefore, passed on the piston 17 by supporting element 23 by the swing that the rotation of swash plate 18 produces, then supported 23 of the rotary component of swash plate 18 discharges.Have only the oscillating motion of swash plate 18 to be converted into the linear reciprocating motion of piston 17 in cylinder 7, the volume of feasible preceding work chamber 15 and back work chamber 16 alternately increases and reduces.

Intake chamber 24 and preceding discharge chamber 25 before front case 1 defines.Between intake chamber 24, main shaft 12 and front case 1, stuffing box bearing 14 is installed, in case the mixture of coolant, for example coolant and oiling agent leaks.Preceding intake chamber 24 is communicated with bent axle chamber 8 by hole on the preceding valve plate 9 and the passage 26 on the cylinder block 3.Discharging chamber 25 then is connected with preceding work chamber 15 by the tap hole 28 on the preceding discharge valve plate 9 on the preceding valve plate 9.

The surface of the preceding valve plate 9 in the preceding work chamber 15 is provided with a sheet of preceding suction valve 29, and this suction valve 29 is opened when piston 17 moves right.The surface of discharging the preceding valve plate 9 in the chamber 25 is provided with a sheet of expulsion valve 30, and this expulsion valve 30 is opened when piston 17 is moved to the left.Expulsion valve 30 is spacing by preceding valve check plate 31.

Rear case 5 limits back intake chamber 32 and discharges chamber 33 with the back.Back intake chamber 32 is communicated with bent axle chamber 8 by hole and the passage 34 on the cylinder block 3 on the valve plate 4 of back.In addition, back intake chamber 32 also is communicated with back work chamber 16 by back inlet hole 35.The back is discharged chamber 33 and is connected with back work chamber 16 by the back tap hole 36 on the valve plate 4 of back.Back suction valve 37, back expulsion valve 38 and back valve check plate 39 all are installed on the valve plate 4 of back in the mode that is similar to corresponding forepiece.

On rear case 5, also be provided with control valve 40 and control chamber 41.Slider 42 is installed in rotation on the main shaft 12 so that can move along the axial direction of main shaft.End near the plat part 20 of main shaft 12 on slider 42 is shaped on a spherical supporting part 43.This sphere supporting part 43 allows the middle body of swash plate 18 to move around the rotational of main shaft 12 and along axial direction.Flange 44 on the slider 42 is connected with an end of sliding sleeve 46 by second thrust bearing 45.

The circular column plug portion 47 that forms in its outer end is arranged on the sliding sleeve 46, and this plunger part 47 is inserted in and in the intake chamber 32 of back chamber is divided into back intake chamber 32 and controls chamber 41.Sliding sleeve 46 also has a cylindrical section 48, and it is coaxial and extended in the cylinder block 3 by plunger part 47 with main shaft 12 and slider 42.The plunger part 48 of sliding sleeve is inserted among the cylindrical section 3d of rear-bank rotor housing 3b slidably.So, sliding sleeve 46 vertically move through second thrust-bearing 45 and flange part 44 passes on the slider 42.Also be provided with first thrust-bearing 49 in the place ahead that is positioned at plat part 20 of main shaft 12, this bearing is stuck between the spacing shaft shoulder 3e that the plat part 20 of main shaft 12 and front air cylinder body 3 be provided with to bear the thrust to main shaft 12.

Shown in Fig. 2 a, piston 17 all has a piston head 17b at its each end.The shape of piston 17 is such, the intermediate portion of piston 17, is that attachment portion 17c is operably connected by the both sides of slide rail 23 with the circumferential part of swash plate 18.The cross section of attachment portion 17 is greatly most semicircle, and two-piston head 17b links together by this part.The supporting part 17d that forms in the 17c of attachment portion is supporting slide rail 23.

The working procedure of compressor below will be described.As shown in Figure 1, engage when transmitting the driving torque from motor car engine main shaft 12 beginnings rotation cylinder block 3 in when above-mentioned magnetic clutch.Main shaft 12 driving arms 19 and swash plate 18 rotate.Because swash plate 18 is tilting with respect to main shaft 12, so along with the rotation swash plate 18 of main shaft 12 produces swing, thereby make piston 17 along with this swing to-and-fro motion in cylinder 7.

As desire the discharge discharge capacity of compressor is remained on highest level, control valve 40 is adjusted to the position that control chamber 41 is communicated with back discharge chamber 33.Be higher than the pressure that is applied to its left side so be applied to the pressure on plunger part 47 right sides of sliding sleeve 46, thereby sliding sleeve 46 is moved to left.Simultaneously, the core of swash plate 18 and slider 42 are moved toward right-hand, slide not to have 42 the left end and the plat part 20 of main shaft 12 enter jointing state thereby make.Because the moving to left of swash plate 18, the convex portion with swash plate 18 of pin 21 moves to left with respect to the plat part 20 of main shaft 12, makes pin 21 elongated holes 22 along plat part 20 be moved to the left.Along with the upper left motion of pin 21, thereby swash plate 18 produces a big tilt angle around spherical supporting part 43 rotations of slider 42.

In addition, piston 17 to-and-fro motion in cylinder 7.Along with the to-and-fro motion of piston 17, coolant is by alternately suction and compression in forward and backward work chamber 15 and 16.

Coolant is entered in the compressor and through forward and backward discharge chamber 25 and 33 by cooling cycle system to forward and backward intake chamber 24 and 32 through crankshaft cavity chamber 8 and is discharged in the cooling cycle system.As mentioned above, swash plate 18 along main shaft 12 move axially to change its tilt angle but its core be located substantially on cylinder 7 in the vertical in the heart.Thereby, along with piston 17 is finished the to-and-fro motion of a stroke, in forward and backward work chamber 15 and 16, avoided the pressure loss.Compressed in the same manner coolant is discharged from from forward and backward work chamber 15 and 16.Thereby, in forward and backward work chamber, producing flowing of coolant, stuffing box bearing 14 contacts with the coolant that should flow, and the cooled liquid of fricative heat of bearing and main shaft 12 is taken away.

As desire to make the discharge discharge capacity of compressor to remain on floor level, control valve 40 is adjusted to the position that control chamber 41 is communicated with back intake chamber 32.When main shaft 12 rotated with this understanding, swash plate 18 moved right piston 17.As the reaction force that imposes on piston 17, one of generation makes the power that the tilt angle of swash plate reduces on swash plate 18.Be the power that piston 17 makes it rotate along counterclockwise direction for 18 1 of swash plates.

Because pin 21 is slidingly matched with elongated hole 22 thereby has limited the power that acts on the swash plate 18, and produce the power that a core that promotes swash plate 18 moves to right along the circumferential direction of main shaft 12.The component of this power is passed to sliding sleeve 46 by slider 42.As mentioned above, owing between the both sides of the plunger part 47 of sliding sleeve 46, do not produce pressure difference, so plunger part 47 moves right.So the tilt angle of swash plate 18 reduces, the core of swash plate 18 is shifted to back work chamber 16 simultaneously.The center stop of back work chamber 16 remains on big to identical position with above-mentioned maximum pump discharge.In addition, all there is an internal surface 300c inboard of each piston 17.The gap that about 2-3mm is arranged between the side face of swash plate 18 and each piston 17.This is that the variable capacity oblique tray type compressor needs bigger gap so that by changing the capacity that piston stroke changes compressor because have.

Regrettably, bigger gap can rotate piston 17 and owing to the bump between the outer circumferential face of the internal surface 300c of piston 17 and swash plate 18 produces noise in cylinder 7.Therefore, all be provided with one on each piston 17 and make one with its core and thus to the anti-rotation device 300 that radially extends.Shown in Fig. 2 a and 2b, anti-rotation device 300 comprises first surface 300a and second surface 300b who forms in its longitudinal end of a surface formation thereon.Groove 310 on the wall of anti-rotation device 300 and each cylinder 7 matches.Because anti-rotation device 300 and the noise that has prevented that thereby the rotation of piston 7 around himself axis from having suppressed to produce cooperating of groove 310 in compressor operation.

Yet in this structure, the surface of the groove 310 of cylinder block 3 and the first surface 300a of anti-rotation device 300 preferably make fine surface by fine-processing technique, so that can slide smoothly mutually.Because groove 310 is positioned at the inboard of cylinder block 3 and the inboard projection that many obstruction grindings are arranged, therefore, need consumption a large amount of time and energy for surface with the groove 310 of lathe and finisher cutting and grinding cylinder block 3.In addition, each above-mentioned surface is all than broad.The productivity of this compressor of result is lower and manufacture cost is higher.

The object of the present invention is to provide a kind of piston compressor, particularly a kind of variable capacity slant plate type compressor, its manufacturing is easy and with low cost.

Another object of the present invention is to provide a kind of piston compressor, particularly a kind of variable capacity slant plate type compressor, a device that prevents piston rotation that durability is strong is arranged on it.

According to piston compressor of the present invention, comprising a compression case, an intake chamber and a discharge chamber with the sealing of bent axle chamber.Compression case comprises a cylinder block that has one group of cylinder.Main shaft is supported in the cylinder block rotationally.A swash plate is connected with main shaft obliquely.By the bearing connection swash plate is connected with one group of piston, thereby when main shaft rotates, but driven plunger to-and-fro motion in cylinder.The some work chamber of formation between the vicinal face of each end of each piston and corresponding cylinder.One is being supported the core of this swash plate obliquely with the supporting part of main shaft coaxial arrangement.Angle control device drives this supporting part along the moving axially of main shaft, thereby the core that promotes swash plate moves axially to change the angle of inclination of swash plate along main shaft.Piston is contained in each cylinder and slidably along with banking motion to-and-fro motion in cylinder of swash plate.A rotation preventing mechanism prevents that each piston is around himself rotational.

Rotation preventing mechanism comprises the first anti-rotation moving part and the second anti-rotation moving part that is arranged in the compression case that form in the heart in piston.The first anti-rotation moving part comprises the slip surface that at least one forms thereon, and fine surface is processed into by fine-processing technique in this surface.The second anti-rotation moving part comprises a slip surface that forms in the peripheral surface of the second anti-rotation moving part.The slip surface of the first anti-rotation moving part slides on the second anti-slip surface smoothly, makes the routing motion of win the rotation inhibiting part and the second anti-rotation moving part can prevent that piston is around himself rotational.

Other purposes of the present invention, feature and advantage will be embodied by means of the detailed description of accompanying drawing to most preferred embodiment of the present invention by following.

Fig. 1 is the longitudinal sectional view of the Wobble plate type refrigerant compressor that has the discharge capacity controlling mechanism of prior art;

Fig. 2 a is the perspective view of a piston in the compressor shown in Figure 1;

Fig. 2 b is the sectional view along the 2b-2b line intercepting of Fig. 1;

Fig. 3 a is the perspective view according to the piston on the piston compressor of the first embodiment of the present invention;

Fig. 3 b is the sectional view along the intercepting of the 2b-2b line on Fig. 1 of expression first embodiment of the invention;

Fig. 4 a is the perspective view that is used in the piston on the piston compressor of second embodiment of the invention;

Fig. 4 b is the sectional view along the intercepting of the 2b-2b line on Fig. 1 of expression second embodiment of the invention;

Fig. 5 a is the perspective view that is used in the piston on the piston compressor of third embodiment of the invention;

Fig. 5 b is the sectional view along the intercepting of the 2b-2b line on Fig. 1 of expression third embodiment of the invention;

Fig. 6 a is the perspective view that is used in the piston on the piston compressor of fourth embodiment of the invention;

Fig. 6 b is the sectional view along the intercepting of the 2b-2b line on Fig. 1 of expression fourth embodiment of the invention;

Fig. 7 a is the perspective view that is used in the piston on the piston compressor of fifth embodiment of the invention;

Fig. 7 b is the sectional view along the intercepting of the 2b-2b line on Fig. 1 of expression fifth embodiment of the invention;

Fig. 8 a is the perspective view that is used in the piston on the piston compressor of sixth embodiment of the invention;

Fig. 8 b is the sectional view along the intercepting of the 2b-2b line on Fig. 1 of expression sixth embodiment of the invention;

Fig. 9 a is two schematic representation that are in the piston in the reciprocal compression movement of expression, and wherein anti-rotation device is according to sliding mutually shown in Fig. 8 a and Fig. 8 b;

Fig. 9 b is a plotted curve, has wherein represented the circumferential end faces of a piston shown in Fig. 8 a and Fig. 8 b and the relation curve of variable in distance between another piston end surface and the variation of swash plate corner.

Most preferred embodiment of the present invention is all similar with compressor shown in Figure 1, and different is the structure difference of the rotation preventing mechanism of the piston in the cylinder.Therefore in order to simplify description to most preferred embodiment, similarly parts all adopt with Fig. 1 in identical mark mark and omitted specific descriptions to like.And although following description to embodiment is relevant oblique tray type compressor, the present invention is not limited in oblique tray type compressor.

The structure of the piston 17 of first embodiment of the invention has been described among Fig. 3 a and the 3b.On each end of piston 17 piston head 17b is arranged.Between the two-piston head 17b of the middle part of piston 17, there is a junction to divide 17c.This attachment portion 17c links together two-piston 17b, and its sectional shape is semicircle basically.In addition, attachment portion 17c is operably connected by the both sides of slide rail 23 with the circumferential part of swash plate 18.Supporting slide rail 23 at the inboard supporting part 17d that forms of attachment portion 17c.An integrally formed with it evagination part 301 is all arranged on each piston 17, this evagination part by the center of the attachment portion 17c of piston 17 radially evagination form an arch.The radial outer end face 301a of evagination part 301 is tapered.Bolt 6 passes front case 1, cylinder block 3 and rear case 5 and is distributed in respectively between each piston 17, it is fused and is parallel to the longitudinal shaft of main shaft 12.Two radial outer end face 301a of evagination part 301 lean slidably on the peripheral surface of bolt 6, make evagination part 301 and cooperating of bolt 6 can prevent that piston 17 is around self rotational.

Fig. 4 a and Fig. 4 b have represented the piston 17 in the second embodiment of the invention.The evagination part 301 that one rectangle can be arranged on the piston 17, its lip-deep its outside of spill that is shaped as at piston 17 then divides the direction of 17c to extend with rectangular shape to the middle interconnecting piece away from piston 17.Have on the evagination part 302 one that form on its surface, the cross section is greatly most semicircle and the groove 302a parallel with piston 17.The peripheral surface 6a of bolt 6 and groove 302a are slidingly matched, and the acting in conjunction of evagination part 302 and bolt 6 can prevent that piston 17 is around himself rotational.

Fig. 5 a and Fig. 5 b have represented the piston 17 in the third embodiment of the invention.A pair of evagination part 303 can be set on the piston 17, and its both sides by the middle part of the attachment portion 17c of piston 17 are wing and extend to both sides.Have on the evagination part 303 one that form on its surface, the cross section is greatly most semicircle and the groove 303a parallel with piston 17.The peripheral surface 6a of bolt 6 and groove 303a are slidingly matched, and the acting in conjunction of evagination part 303 and bolt 6 can prevent that piston 17 is around himself rotational.

Fig. 6 a and Fig. 6 b have represented the piston 17 in the fourth embodiment of the invention.The evagination part 304 that one rectangle can be arranged on the piston 17, its lip-deep its outside of spill that is shaped as at piston 17 then divides the direction of 17c to extend with rectangular shape to the middle interconnecting piece away from piston 17.On housing 3, fixed the ring part 50 of a shape such as annular slab sample.A rectangle groove 50a who cuts out from its inboard is arranged on ring part 50.The peripheral surface 304a of the evagination part 304 of piston 17 cooperates slidably with the surperficial 50d of the rectangle groove 50a of ring part 50, and ring part 50 can prevent that with the acting in conjunction of the evagination part 304 of piston 17 piston 17 is around himself rotational.

Fig. 7 a and Fig. 7 b have represented the piston 17 in the fifth embodiment of the invention.On each piston 17 rectangle groove 305 can be arranged, it is shaped as spill and extending axially along the attachment portion 17c of piston 17 piston 17 lip-deep.Also has an evagination part 50b who inwardly radially extends by ring part on the ring part 50.The peripheral surface 50c of the evagination part 50b of ring part 50 and the groove 305 of piston 17 are slidingly matched, and make the ring part 50 and the acting in conjunction of groove 305 can prevent that piston 17 is around himself rotational.

Fig. 8 a and Fig. 8 b have represented the piston 17 in the sixth embodiment of the invention.All have one to make one with the attachment portion 17c of piston 17 and on each piston 17 by the radially outer evagination part 306 that moves into arch in its center.Longitudinal end at evagination part 306 forms an end face 306a.The end face 306a that each end face 306a of evagination part 306 is adjacent fits, and makes when piston 17 to-and-fro motion, and adjacent end face can slide mutually.

The surface of the above-mentioned various anti-rotation devices that on piston 17, form, all use in the fine finishing process as radial end face part 301a, Fig. 4 a among Fig. 3 a and Fig. 3 b and groove 302a, Fig. 5 a among Fig. 4 b and groove 303a, Fig. 6 a among Fig. 5 b and outer circumferential surperficial 304a, Fig. 7 a among Fig. 6 b and the groove 305 among Fig. 7 b and the axial end 306a among Fig. 8 a and Fig. 8 b and to grind or polishing processing, so that obtain meticulous surface.The surface roughness of these fine surfaces (R μ) should be less than 1.6 μ m(ANSIB46.1-1978).Meticulous like this surface can improve above-mentioned anti-slip device with Fig. 3 a to Fig. 5 b in peripheral surface 6a or the peripheral surface 50c of the evagination part 50b of peripheral surface 50d, Fig. 7 a of the slot portion 50a of the ring part 50 among bolt 6, Fig. 6 a and the 6b and the ring part 50 among the 7b and the axial end 306a among Fig. 8 a and the 8b anti-adhesion property and the wear resistance when sliding.In addition, the peripheral surface 50c of the evagination part 50b of the peripheral surface 50d of the slot portion 50a of the peripheral surface 6a of bolt 6, ring part 50 and ring part 50 all is processed into above-mentioned fine surface.For enough slidably property, wear resistance and durability are provided, after fine finishing, can also carry out surface treatment to these surfaces, handle as teflon plating, chromium plating processing and ceramic coating.

Thereby, in the present invention, because the piston 17 of anti-rotation device all is designed to and is fixed in the cylinder block 3 or the anti-rotation moving parts of bolt 6 partly slide among each embodiment, thereby above-mentioned needs are processed into the area of slidably surface of contact of fine surface less than the surface of contact area of prior art.In addition, owing to adopted other parts, slidably contact preventing piston 17 around self rotational as the ring part 50 and the anti-rotation device of above-mentioned piston 17, thereby portion need process the internal surface of cylinder block 3 with finisher.

In addition, according to Fig. 9 a and 9b, the sliding process between the axial end part 306a that the axial end part 306a of evagination part 306 is adjacent among the 6th embodiment shown in Fig. 8 a and the 8b is shorter than the process that each surface of contact among first to the 5th embodiment slides mutually.The reason that sliding process shortens is, the to-and-fro motion of the piston 17 that piston 17 is adjacent ' together thereby or before bottom dead center when the top dead center at piston arrives middle part, the axial end of piston 17 and adjacent piston 17 ' axial end between distance A keep constant, axial end portion 306a and adjacent axial end 306a ' just just had of short duration level and smooth slip before or after the top dead center of piston 17 or adjacent piston 17 ' in the middle part of arriving respectively or lower dead center in addition.Therefore, reduced effectively anti-rotation device, as the wear phenomenon of crossing of

axial end portion

306a and 306a '.

Although be to describe of the present inventionly by means of most preferred embodiment here, the present invention is not limited to these contents.Be understood that, by means of the change of the ordinary skill of prior art with improve the present invention and obviously will fall in the claim of the present invention institute restricted portion.

Claims

1, a kind of piston compressor, comprising:

The compressor housing that the bent axle chamber is closed, an intake chamber and a discharge chamber in this housing, described compressor housing comprises a cylinder block;

In described cylinder block, form one group of cylinder;

Be mounted slidably one group of piston in each described cylinder, each piston all has a corresponding axis;

In described cylinder block, supporting a main shaft rotationally;

One swash plate is connected with described main shaft obliquely;

One bearing is connected described swash plate with described piston, make when described swash plate rotates and can drive the to-and-fro motion in described cylinder of described piston;

At least one work chamber that limits by an internal surface of end face of described each piston and described cylinder;

One coaxial and supporting the supporting part of the core of described swash plate obliquely with described main shaft;

Tilt angle control gear drive described supporting part move axially along described main shaft make described swash plate core along described main axle moving, thereby change the angle of inclination of described swash plate, described piston is along with the banking motion of described swash plate is reciprocating; And also have

An anti-rotation device that prevents described each piston around corresponding rotational, described anti-rotation device comprises the first anti-rotation moving part and the second anti-rotation moving part that is arranged in the described compressor housing that form in the heart in described piston, the described first anti-rotation moving part has first slidingsurface that forms at least thereon, described first slidingsurface is processed to fine surface, the described second anti-rotation moving part has second slidingsurface that forms at least thereon, first slidingsurface of the described first anti-rotation moving part slides on described second slidingsurface of the described second anti-rotation moving part smoothly, described first anti-rotation moving part and the described second anti-rotation moving part acting in conjunction are to prevent that described each piston is around described corresponding rotational.

2, piston compressor as claimed in claim 1 is characterized in that, the described first anti-rotation moving part comprises an evagination part that is extended by described piston center, and the described second anti-rotation moving part comprises rotation inhibiting parts that are fixed in the described compressor housing.

3, piston compressor as claimed in claim 2 is characterized in that, the described first anti-rotation moving part also comprises a groove that forms thereon.

4, piston compressor as claimed in claim 2 is characterized in that, the described second anti-rotation moving part also comprises a bolt that described compressor housing and described cylinder block are coupled together.

5, piston compressor as claimed in claim 2 is characterized in that, the described second anti-rotation moving part also comprises a ring part that is fixed in described compressor housing inboard.

6, piston compressor as claimed in claim 5 is characterized in that, the described second anti-rotation moving part also comprises that form and corresponding with each a cylinder evagination part on described ring part.

7, piston compressor as claimed in claim 1 is characterized in that, the described first anti-rotation moving part also comprises a groove that is formed centrally in described piston.

8, piston compressor as claimed in claim 7 is characterized in that, the described second anti-rotation moving part also comprises a ring part that is fixed on the inboard of described compressor housing.

9, piston compressor as claimed in claim 8 is characterized in that, the described second anti-rotation moving part also comprises a groove that forms corresponding to each cylinder on described ring part.

10, piston compressor as claimed in claim 1 is characterized in that, described first slidingsurface of the described first anti-rotation moving part is processed to fine surface, and its surface roughness is less than 1.6 μ m.

11, piston compressor as claimed in claim 1 is characterized in that, described second slidingsurface of the described second anti-rotation moving part is processed to fine surface, and its surface roughness is less than 1.6 μ m.

12, piston compressor as claimed in claim 1 is characterized in that, described first slidingsurface of the described first anti-rotation moving part and described second slidingsurface of the described second anti-rotation moving part are processed to fine surface, and its surface roughness is less than 1.6 μ m.

13, piston compressor as claimed in claim 1 is characterized in that, described compressor is an oblique tray type compressor.

14, a kind of piston compressor, comprising:

In described cylinder block, form one group of cylinder;

In described cylinder block, supporting a main shaft rotationally;

-swash plate is connected with described main shaft obliquely;

-bearing is connected described swash plate with described piston, make when described swash plate rotates and can drive the to-and-fro motion in described cylinder of described piston;

An anti-rotation device that prevents described each piston around corresponding rotational, described anti-rotation device comprises an anti-rotation moving part that forms in the heart in described piston, described anti-rotation moving part has two slidingsurfaces that form, that have fine surface of two radial end faces at described piston at least, described each slidingsurface of described anti-rotation moving part slides on the adjacent sliding surface on its adjacent anti-rotation moving part smoothly, described anti-rotation moving part and the acting in conjunction of described adjacent anti-rotation moving part are to prevent that described each piston is around described corresponding rotational.

15, piston compressor as claimed in claim 14 is characterized in that, the described slip surface of described anti-rotation moving part all is processed to fine surface, and its surface roughness is less than 1.6 μ m.

16, piston compressor as claimed in claim 14 is characterized in that, described compressor is an oblique tray type compressor.

17, a kind of piston compressor, comprising:

In described cylinder block, form one group of cylinder;

In described cylinder block, supporting a main shaft rotationally;

-swash plate connects with described main shaft obliquely and rotates with described main shaft;

An anti-rotation device that prevents described each piston around corresponding rotational, described anti-rotation device comprises the first anti-rotation moving part and the second anti-rotation moving part that is arranged in the described compressor housing that form in the heart in described piston, the described first anti-rotation moving part has first slidingsurface that forms at least thereon, described first slidingsurface is processed to fine surface, the described second anti-rotation moving part has first slidingsurface that forms at least thereon, first slidingsurface of the described first anti-rotation moving part slides on described second slidingsurface of the described second anti-rotation moving part smoothly, described first anti-rotation moving part and the described second anti-rotation moving part acting in conjunction are to prevent that described each piston is around described corresponding rotational.

18, piston compressor as claimed in claim 17 is characterized in that, described compressor is an oblique tray type compressor.